Means for forming windowed apertures



June 2, 1942. E. 'r. JAEGER ETAL 2,284,872

MEANS FOR FORMING WINDOWED APERTURES Filed March 23, 1959 15Sheets-Sheet 1 INVENTORS. Huperf LoefflqrJr. Lou/.5 Bischo/f' ATTORNEYS.

June 2, 1942.

E. 'r. JAEGE R ETAL MEANS FOR FORMING WINDOWED APERTURES FiledMarch 23,1959 13 Sheets-Sheet 2 Lo s Blschof'f" y E dwardT M ATTORNEYS June 2,1942. E. 1'. JAEGER ETAL MEANS FOR FORMING WINDOWED APERTURES I FiledMarch 23, 1939 13 Sheets-Shet 3 J1me 1942- E. 1'. JAEGEl i z-rm.2,234,372

MEANS FOR FORMING WINDOWED APERTURES Filed March 23, 1939 13Sheets-Sheet 4 1N VENTORS.

ATTORNEYS.

June 2, 1942. E. TQJAEGER ETAL 2,234,372

MEANS FOR FORMING WINDOWED APERTURES FiledMarch 23, 1939 l3 Sheets-Sheet5 E l h "In!" Q BY EdwardZ'Ja er W ouw ATTORNEYS:

June 2, 1942. E. 'r. JAEGER ETAL MEANS FOR FORMING WINDOWED APERTURESFiled'March 23, 1939 13 Sheets-Sheet 6 INVENTORS. Rupert- Loe'ff'ler'Jl:Louis Bl'schoff BY W Edward)? eger M w 144 ATTORNEYS.

June 2, 1942. E. T. JAEGER ETAL MEANS FOR FORMING WINDOWED APERTURESFiled March 25. 1939 13 Sheets-Sheet 7 INVENTORS fiu erf Loeff'ler J'r.Lou/s B/schof'f' Edward Fig18 June 2, 1942. i E. T. JAEGER ETAL MEANSFOR FORMING WINDOWED APERTURES Filed March23, 1939 13 Sheets-Sheet 8INXENgQ/RSlI Ru er!" 0e 1: Lofiis Else/10; EdwardZ'Jaeger ATTORNEYS,

June 2, 1942. E. T. JAEGER ET AL MEANS FOR FORMING WINDOWED APERTURESFiled March 25, 1939 1s Sheets-Sheet 9 fiup Lou/s BLsch W Edwar June 2,1942. E. 'r. JAEGER ETAL MEANS FOR FORMING WINDOWED APERTURES 13Sheets-Sheet 1o Filed March 23, 1939 5-lllllllllllllllllllllllllllllllllllvilli/14g n 1,.

INVENTORS. Ruperl' Loeff/erfi: Lou/s B/schoff' BY WW rfaeger' 9'- MATTORNEYS.

June 1942- E. 1'. JAEG'ER ETAL 2,284,872

MEANS FOR FORMING WINDOWED APERTURES Filed March 23, 1939 1-3Sheets-Sheet 12 807 J04 6 5%: as 85 I I v fl-Ill INVENTORS RupertLoeffZer-Jn Louis Bischof'f EdwardZ'Jaeger ATTORNEYS.

Patented Junc z,

MEANS FOR FORMING WINDOWED APERTURES Edward T. Jaegcr, Rupert Loefller,Jr., and Louis Bischoft, New York, N. Y., assign ore to Oneida PaperProducts, Inc., New York, N. Y., a corporation of New York ApplicationMarch 23, 1939, Serial No. 263,648

8 Claims.

This invention relates to apparatus and means for the formation ofsheets, bags or containers of various kinds, and particularly relates toapparatus for forming transparent windows or other openings in acontinuous web of material, such web being thereafter used for theformation of the aforementioned articles.

In the formation of transparent openings in a continuousweb, it isnecessary first to exercise a portion of the material forming theopening and thereafter, to cover such opening with a patch oftransparent material including transparent regenerated cellulosematerial such as Cellophane, Sylph-wrap or the like.

Where a continuous web of sheet material such as paper or othersubstance is to be thus provided with a series of transparent windows oropenings, the web to be thereafter cut up and formed as may be desired,there has heretofore been difficulty in providing means for cutting theopening without interfering with the movement of the web of sheetmaterial or without tearing any portion of such web. Various means suchas, for instance, halting the progress of the web at the moment the cutis made or providing a I the web to permit the cutting operation to takeplace, then extreme difllculty is experienced in obtaining properregister of the edges of the sheets in relation to the cut-out orperforation to be made. The necessary sudden cessation of movement ofthe web and the sudden recurrence of movement thereof often tends towrinkle and distort the sheet so that the cut-out or perforation may beirregular or the sheet itself may be torn or distorted.

In the case of a machine having a cutting knife in a rotating cylinder,it may be necessary to use the same size slot on a bag or sheet ofdifferent lengths. This cannot be done unless the rotating cutting knifecylinder is changed to the required diameter for each length of bag orsheet. Therefore, no unanticipated sizes could be quickly manufacturedowing to the necessity for first making a cutting cylinder having acircumference exactly equal to the new sizes desired.

Objects of this invention. therefore are to provide in an apparatus forforming an opening or a transparent window in sheet material, meanswhereby a continuous web of such sheet material may be cut, perforatedor slotted with openings of predetermined size and in predeterminedrelation to each other without any variation in the speed or movement ofthe web of sheet material.

Further objects of this invention are to provide means for varying thedistance between cutouts, perforations or slots formed in a continuousweb of sheet material without the necessity for any change in themechanism forming the cutouts, without any requirement for additionalspecial or multiple parts for such mechanism (such parts beingsubstantialduplicates for each other except as to size) and without thenecessity for continually stopping, altering and adjusting the machine.

Heretofore it has been extremely diflicult in the manufacture oftransparent openings in sheet-material to perform the operation ofcutting the opening and ailixing the transparent material at the openingin a single continuous automatic operation. Difficulties have arisen inregistering the cut-out portion exactly with the transparent material tobe applied over such cutout. Further difliculties have arisen owing tothe fact that the transparent material to be applied over the openingwas to be applied in patches, that is, in cut-off lengths; while the webupon which such patches were to be applied was a continuous movingsheet.

Accordingly, further objects of this invention are to provide apparatusby means of which the continuously moving web may, after it has beenslotted or perforated or after the cut has been performed, have suchcut-out covered by a transparent patch without any interruption of theoperation or without any necessity for manual manipulation.

Still further objects of' this invention are so to arrange the mechanismthat, instead of the necessity for applying a series of patches upon thematerial surrounding the cut-out or perforation, the material formingthe transparent window may be supplied to the machine in a continuousroll, the machine cutting patches from such continuous roll and causingsuch patches to adhere to the material surrounding the cut-out in afully automatic operation.

Another object of this invention is so to construct the mechanism whichapplies the transparent patch to the cut-out as to provide simplifiedmeans for quickly changing either the length of the patch to be appliedor the distance between the patches applied in accordance with anyvariations in the size of slot or cut-out and/or the distance betweensuch cut-outs.

Other objects of this invention are to eliminate the changing of dies orknives, where the same Figure 2 is a corresponding side elevational viewof the mechanism of Figure 1 taken on the opposite side of themechanism.

Figure 2a corresponds to Figure 2 and is a schematic perspectiverepresentation of the various parts of the mechanism.

Figure 3 is a top elevational view of the mechanism of Figure 2 takenalong the line 33 of Figure 2, and looking in the direction of thearrows.

Figure 4 is a top elevational view of the mechanism of Figure 2 takenalong the line 4-4 of Figure 2 and looking in the direction of thearrows.

Figure 5 is a sectional elevation taken along the line 5-5 of Figure 3and looking in the direction of the arrows.

Figure 6 is a sectional elevation taken along 6-6 of Figure 5 andlooking in the direction of the arrows.

Figure 7 is a sectional elevation taken along the lines of Figure 6looking in the direction of the arrows.

Figure 8 is a sectional elevation taken on the lines 8-8 of Figure 3 andlooking in the direction of the arrows.

Figure 9 is a sectional view taken along 9-9 of Figure 8 and looking inthe direction of the arrows.

Figure 10 is a fragmentary view of a modified form of the oscillatingmechanism of the punching means and corresponds to the members I58 andI43 of Figure 5.

Figure 11 is a fragmentary end view of one form of the oscillating meansof Figure 10 and corresponds -to the members I58 and I43 of Figure 8.

Figure 12 is a sectional elevational taken along the lines l2-I2 ofFigure 8 looking in the direction of the arrows.

Figure 13 is a cross-sectional taken along l3| 3 of Figure 10 looking inthe direction of the arrows.

Figure 14 is a cross sectional view taken along the line I4-l4 of Figure10 looking in the direction of the arrows.

Figure 15 is a sectional elevation taken along the lines l5|5 of Figure4.

Figure 16 is fragmentary view of Figure 15 showing the clutch orcoupling in further detail.

Figure 1'7 is a sectional view taken on the line I'L-H of Figure 3looking in the direction of the arrows.

Figure 18 is a cross sectional view taken along lines |8l8 of Figure 2.

Figure 19 is a sectional view taken along the lines l9l 9 of Figure 18.

Figure 20 corresponds to Figure 19 showing the mechanism thereof in adifferent position to be hereinafter explained.

Figure 21 is a cross sectional view of the cutting mechanism taken on2l2l of Figure 4.

Figure 22 is an elevational view of the suction roller taken along theline 2222 of Figure 21.

Figure 23 is a cross sectional view taken along 23-23 of Figure 22.

Figure 24 is a cross sectional view taken along 24-24 of Figure 22.

Figure 25 is a cross sectional view along lines 25-25 of Figure 23.

Figure 26 is a cross sectional view along 26-26 of Figure 23.

Figure 27 is a sectional elevation taken along 2'|--2| of Figure 4.

Figure 28 is a sectional elevation taken along 2828 of Figure 1.

Figure 29 is a sectional elevation taken along line 2929 of Figure 1.

Figure 30 is an elevational view taken along 30-30 of Figure 1.

Figure 31 is a cross sectional view taken along 3l3l of Figure 8. t

Figure 32 is a cross sectional view taken along 32-32 of Figure 10.

Figure 33 illustrates a continuous web having a transparent windowformed therein.

Figure 33a shows said web cut and folded to produce the bag of Figure34.

Referring now to Figures 1, 2 and 2a, the main roll of sheet material50, in which transparent windows are to be formed, is mounted uponrollers 5| which in turnare mounted in the bifurcated member 52 and isfree to rotate therein.

The sheet material or web 53 may be threaded through the machine invarious different ways. The machine here illustrated provides for atleast three operations, to wit: The printing of the main web, theperforation or cutting out of an opening therein thereof, and theapplication of a transparent sheet or patch at the perforated or cut-outpoint. These operations may be performed in any desired order, orcertain of these operations may be omitted. The order in which theseoperations are performed is determined by the manner in which the paperor sheet 53 taken from the roll 50 is threaded through the variousportions of the machine.

It should be noted that, in the description hereinafter set forth, theprinting rolls or mechanism are not an essential part of the machine;but are shown schematically in their relation to the machine whichcomprises the invention herein.

In many cases, it is desirable merely to effect the cut-out, apply thetransparent patch thereon and reserve any printing operation for anylater manufacturing operation that may be necessary. In the event thatit is so desired merely to form the window without any printing matterwhatsoever upon the sheet, itself, the web 53 is threaded along the pathA (indicated by dotted lines) past the idling roller 54 whereby thedirection of the moving sheet is changed. The direction of the movingsheet is again changed by the idling roller 55 directly above the roller54 and the web 53 then is moved past the feed roller 56 whence ittravels over the idler 51 and into and through the punching mechanism58.

Owing to the fact that the web or sheet 53 must pass through variousdifferent processes and apparatus in its passage through the ma, chineitself, it is necessary especially where the web is not of great tensilestrength to provide feed rollers giving it a forward impetus in itsvarious movements, rather than to rely merely on the pull at the end ofthe web as it emerges from the machine. For this purpose, the roller 56is not an idling roller but a driven one as hereinafter described.

The machine itself is driven by means of the belt 59 which is connectedwith any desired motive power and which drives the pulley 68. Thepulley'68 in turn drives the shaft 6| which in turn causes the pinion 62to rotate thus driving the gear 63 which through the bevel gears 64 and65 causes the shaft 66 to rotate in its bearings 61, 61, friction beinggreatly reduced by the thrust bearings 68, 68. l I

The bevel gear 69 at the opposite end of the shaft 66 meshes with thebevel gear 18 which thus causes the shaft 1| to rotate. The rotation ofshaft 1| drives the change gear wheel 12 which in turn drives the idlinggear wheel 13 which drives the gear wheel 14 whereby the gear wheel 15is rotated, thereby rotating the shaft 16 and thus causing the rubberroller 11 to rotate. The roller 56 is mounted on the shaft 18 (see alsoFigure 1) which is rotated by the gear wheel 14.

Thus the feed roller56 and the corresponding roller 11 capture the web'of sheet material 53 between them and cause the web to move on towardsthe punching mechanism 58.

Where printing rolls are to be used, gear 19 driven by shaft 18 drivesidler 88 which is free to turn on shaft 1|. Sprocket 588 attached togear 88 drives the printing rolls 58l through the sprocket chain 582. Itwill thus be clear that any change in the speed of the feed rolls willresult in a change of speed of the printing rolls.

Where it is necessary to thread the web of sheet material 53 through therollers 56 and 11,

ting the ready insertion and threading through of the web 53. Such meansfor raising the rubber roller 11 comprises slidable mountings 83, 83(Figures 18, 19 and 20) for the shaft 16. Such slideable mountings 83are captured within'the stationary member 84 (Figures 19 and 20) saidstationary member 84 having slots 85, 85 within which the slidablemounting 83 may travel.

The slidable mounting does not rest directly upon the interior base 86of the stationary member 89 but a coil spring 81 under compression isprovided between the base 86 and the slidable mounting 83. The upper endof the slidable mounting 83 is provided with a series of bevel studs 88,88 separated from each other by spaces approximately equal to or greaterthan their diameter. As seen in Figures 19 and 20, it will be obviousthat the depression of the slidable mounting 83 will cause the rubberroller 11 to more closely approach the feed roller 56 while a raising ofthe slidable mounting 83, as seen in Figure 20, will correspondinglycause the gap 8| between the rubber roller 11 and the roller 56 toincrease and provide sufficient space for the threading of the paper.Since the spring 81 is a compression spring, in its normal condition, itwould tend to maintain the slidable member 83 at or near the uppermostpart of the member 84 thus tending, when the pressure on such spring isreleased, to drive the rollers 11 and 56 apart. The compression spring81 is maintained under compression, however, by the fact that bevelstuds 89 mounted upon the rotatable member 98 register end to end andpress against the bevel studs 88 of the slidable mounting 83 (as inFigure 19). When the rotatable member 98 is turned upon its shaft 9| sothat the upper bevel 'studs 69 no longer register end to end with theroller bevel studs 88 but instead register with the spaces between them,then the slidable mounting 83 is forced up by compression spring 81, adistance equal to the axial length of on set of bevel studs until thestuds bear against the base of the opposite member, and the rollers 11and 56 are separated. In order to facilitate the rotation of the shaft9| and the consequent rotation of the rotatable member 98 and itsassociated bevel studs 89, a handle 92 is attached to the rotatableshaft 9| by means of the collar 93.

Since the shaft 16 extends from one side to the other of the machine,the mountings 82 on each side of the machine as seen especially inFigure 18 are exactly similar and the turning of the two correspondinghandles 92 simultaneously will cause the shaft 16 to rise evenly and inthe same plane and will thus cause the rubber roller 11 to rise.

In order to insure that the handles 92, 92 on either side of the shaft16 will be rotated simultaneously so that the shaft will rise evenly andin the same plane, a link 94 is mounted between the two handles 92, 92and is hingedly connected to each handle by pivots 95, 95. It will thusbe obvious that rotation of either handle 92 will through the link 94communicate the same motion to the corresponding handle at the oppositeend and will thus cause both ends of the shaft 16 to risesimultaneously. Likewise the provision of the link 94 makes it possibleto cause the shaft to rise by manipulating either of the handles 92 oreven by grasping any portion of the link 94 causing it to move in thedesired direction.

After the paper or web is properly threaded through the gap 8| (Figure20), then the handles 92 or the link 94 may be rotated or pushed in adirection opposite to that in which they had previously been moved andthe shaft 16 and its rubber rollers 11 will thereby be depressed andwill engage the web 53 between the rollers 11 and 56. The bevel studs 88and 89 are so arranged that lateral pressure of a stud on one memberagainst a stud on an adjacent member will cause the stud on the movablemember 83 to slide down, thus causing the movable member 83 to slidedown and thus causing the studs to register with each other endto endrather than side to side. The bevelling of the studs must therefore beat such angle or curvature as to permit this slidin arrangement to takeplace.

The rollers 56 and 11 thus feed the paper forward over the idling roller51 into the punching mechanism 58.

Although we have here described in detail one way of separating the feedrollers to permit threading of the web through the machine, it of coursewill be clear that any other suitable means may be used which willseparate such rollers for threading purposes and then bring themtogether to perform the feeding operation.

The punching mechanism (see Figures 2, 5 and 8) comprises a movableplatform 96 which is mounted at either lateral edge thereof upon freerollers 91 (see also Figures 6 and 7) which in turn are mounted in atruck 98. The free rollers 91 thus carry the movable platform 96 uponthe upper portions of the rim thereof, the lower portions of the rollers91 riding in the track 99 which is attached by the bracket I88 to theframe I81. A rack 182 is also mounted beneath the movable platform alongthe lateral ends thereof, said rack being mounted immediately above acorresponding rack I03 which is mounted in the bracket I00. A pinion I04is rotatably enmeshed between the two racks I02 and I03 and thus assuresthat the movable platform 96 will at all times register accurately withthe mounting bracket I00, the free rollers 91 being provided merely forthe purpose of reducing friction.

The movable platform 96 carries, securely at tached thereto, thevertically arranged arms I05 and I06 (see Fig. 8). V-shaped tracks orslots I01-I08 are mounted in the lateral edges of the upper ends of eachof the arms I05 and I06 (see Figures 8 and 9). The punching plate I09,Figure 8, is mounted upon a slidable member H0, the ends of which III,III (see also Fig. 9) are shaped to ride in the tracks I01 and I08.Upward and downward reciprocating motion of the slidable member H in thetracks I01 will obviously result in corresponding upward and down wardmotion of the punching plate I09. Such reciprocating motion isaccomplished in the following manner: Brackets H2, H2 are securelyattached to the upper end of the arm I06, I06. Shaft II3 rotates in amanner hereinafter described in the bearings H4, H4 which are carried bythe brackets I I2, II2; cam H5 is mounted at one end of shaft H3 andthus rotates therewith. A link I I6 is rotatably attached to the cam II5by the eye H1. The opposite end of the link H6 is rotatably attached bymeans of the yoke IIO to the slidable member IIO. A slot II9 permits thelink I I6 to pass through the upper covering I of the chamber I2I inwhich the slidable member rises and falls.

It will now be obvious that rotation of the shaft H3 and thecorresponding rotation of the cam II5 will, through the rotatable eyeII1, cause the link II6 to reciprocate vertically and thereby cause theslidable member IIO to correspondingly move up and down thus causing thepunching plate I09 to operate.

A counter-weight I22 may be mounted on the shaft I I3 to compensate forthe weight of the sliding member II 0 and its associated punching plateand to avoid any vibration or friction which may occur due to the weighton the cam II5.

An opening I23 is formed in the movable platform 96 and a plate I24 issecured to said platform 96 surrounding said opening I23 and having alsoan opening I25 surrounded by the female die I26 which exactly matchesthe punching plate I09. It will now be obvious that when the moving web53 passes beneath the punching plate I09 and over the die I26 aperforation will be made in the web 53 by the pressing down of thepunching plate I09 into the die I26, owing to the rotation of the camH5, and the material I21 thereby excised will be thrown down into thefunnel I28.

In order to ensure that the material I21 will be pressed down and awayfrom the cutting edges of the die I26, small plungers I29, I29 may bemounted on the under surface of the punching plate I09, the ends of theplungers being forced to' project beyond the face of the punching plateby the springs I30. By this means, the plungers I29 will press againstthe center portion of the material I 21 to be excised but neverthelessthe springs I30 will permit such pressure to be a yielding and lightpressure which will not tear the paper web 53; but when the material I21has been cut from the web 53 by the operation of the punching plate I09and the die I26, the compression of the springs I30 will permit theplungers I29 to be extruded from the face of the punching plate I09 andthus force the material I21 away from the edges of the die I26 so thatthe cutting edges will be free to receive the punching plate when thenext perforation is made.

The web of sheet material 53 may be held perfectly flat, during thecutting operation and during all of the time that the punching p ate I09is beyond the surface of web 53, by means of a. plate I3I which may beprovided near the under face of the punching plate I09; said plate I3Ihaving an orifice I32 which is slightly larger in each dimension thatthe corresponding dimension of the punching plate. The said plate ismounted upon the slidable mounting IIO by means of the springs I33. Whenthe slidable member H0 is forced downwardly by the action of the camII5, the plate I 3| will come in contact with the web 53 eithersimultaneously with or before the face of the punching plate I09 andwill thereby press the paper against the upper surface of the die I26and thus prevent any breaking, tearing or distortion which may be causedby the subsequent entry of the punching plate I09 through the paper 53and into the die I26. When the slidable member IIO thereafter begins torise and withdraw punching plate I09, the plate I3I will neverthelessremain in contact with the web 53, pressing it against the outer surfaceof the die I26 at least until the punching plate I09 is fully withdrawnfrom the die I26 and from the outer surface of the web 53. By thismeans, any stresses or strains at that portion of the paper which isbeing cut is completely limited to that portion of the web alone and isnot transmitted to any other portion of the web, and thus does notinterfere with the motion of the web or with the smoothness of themovement thereof.

The punching mechanism as a whole is mounted on the movable platform 96for the purpose of permitting the punching plate I09 and the die I26 totravel with the web 53 at the same speed as the web during the cuttingoperation, that is, during the period that the punching plate is beyondand beneath the upper surface of the web 53. The movable platform isthus so arranged that during the period immediately before the cuttingoperation is to take place, the entire punching mechanism is in theposition shown by the dotted lines of Figure 5; and thereafter, duringthe cutting operation, the entire punching mechanism travels on itsplatform 96 to the position shown by the solid lines of Figure 5 andeven beyond if necessary, simultaneously making the perforation orincision required and then rising from surface of the web. The web isthus perforated as it travels along and it is not necessary to stop themotion of the web in order to perform the perforating operation.Likewise, the mounting of the punching mechanism on the movable platform96 is such that immediately after the perforating operation takes place,the entire punching mechanism may be returned to the position shown bythe dotted lines of Figure 5 in order that it be ready for the nextpunching operation.

One form of mechanism by which this oscillatory movement of the platform96 is accomplished is shown in Figure 2 at I34 and in Figures 5 and 8and especially Figures 15 and 16. A gear wheel I35 is rotatably mountedon the shaft 6| in such manner that rotation of shaft 6| will notnecessarily cause rotation of said gear wheel. A clutch mechanism 600(Figs. 15 and 16) is so arranged, however, that a pull on the handle 60Iit serves as a safety device are hereinafter described. The bevel gear Imounted at the oppositeend of the shaft I38 drives the bevel gear I42which in turn drives the shaft I43 (see also Fig. 8). The shaft I43rotates in the bearings I44 and I45, the latter bearing I45 beingmounted on the post I46. An armI41 (see Figs. and 8) is fixedly attachedto the opposite end of the rotating shaft I43 and rotates therewith. The

' said arm' I41 (see particularly Fig. 5) has a slot I48 at the free endthereof. 'A glider I49 is mounted on the end of the arm I41 by means ofthe shaft I50 and the washer I5I, said shaft extending from the gliderI49 through the slot I48 and to the washer I5I, the edges of the slotI41 being captured between the sides of the glider I49 and the washerI5I. The said washer is held in place on its shaft by the nut I52.

It will now be clear that rotation of the shaft I43 as before described,will cause the rotatable arm I41 to rotate and will thus likewise causethe glider I49 to rotate therewith, the glider belng free, however, tooscillate within the slot I48.

The shaft I50 extends through the glider I49 to the opposite sidethereof into the annular groove I53 (see particularly Fig. 8 as well asFig. 5) which is formed in the circular plate I54 (see also Figures 12and 31), said circular plate I54 being supported in fixed unrotatableposition by the bar I55 carried by the post I56. The end of the shaftI50 projecting into the annular groove I53 carries, at that portionwhich rides within said annular groove, a rotatable wheel I51, saidrotatable wheel I51 providing a friction reducing bearing surfacebetween the shaft I50 and the sides of the annular groove I53. It willnow be clear that as the rotatable arm I41 turns, the glider I49 turnswith it but by reason of the freedom allowed to it by its mounting inthe slot I48, the said glider in its rotation is free to be guided bythe wheel I51 as it rides in the annular groove I53 and thus follows apath given it by the annular groove. A slotted arm I58 is pivotallyattached by means of the yoke I59 to the under side of the movableplatform 96 at I60, I60. Said slotted arm is also pivoted about theshaft I6I by means hereinafter described. I

The lower end of the slotted arm is captured by the glider I49. Theglider I49 as seen in Figures 5 and 8, has two rail portions I62, I63surrounded by the lips I64; the glider I49 rides within the slot I65 ofthe arm I58, the rails I62 and I63 engaging the sides I66, I66 of theslot I65, the lips I64, I64 capturing the sides I61, I61 between them. i

The pivotal mounting of the arm I58 on the shaft I6I above referred tois a slidable one effected by the glider I68. The glider I68 has railsI69, I and corresponding lips "I which cooperate to capture the sidesI61 of the movable arm in the same manner as the rails and lips of theglider I49. The glider I68 is free to rotate about the shaft I6I but theshaft I6 I is fixedly mounted in its bearings I12, I12 and does notpermit any other motion than that of simple rotation by the glider I68.It will now be clear that rotation ofthe arm I41 will cause acorresponding rotation of the glider I49. The movement ofthe glider I49will be controlled however, not only by the rotatable arm I41 and theslot thereof I48, but also by the path followed by the wheel I51 in theannular groove I53; so that with respect to the rotatable arm and itsslot if the annular groove is slightly eccentric, then the glider I49will slide back and forth in the slot I48.

The rotation of the glider with the rotatable arm I41 and the pathfollowed by the glider owing to the mounting of the wheel I51 in theanular groove I53 ,will cause a corresponding movement of thelowerportion of the slotted arm I58. Thus, when the rotatable arm hasrotated from the position shown by the solid lines of Figure 5 throughan arc of 180 to the position shown by the dotted lines therein, thelower end, of the slotted arm I58 will have been also moved to theposition shown by the dotted lines. Since the slotted arm I56 is also,pivoted about the glider I69 as a fulcrum then the opposite end of theslotted arm comprising the yoke I59 will have been moved in a directionopposite to that in which the lower end of the slotted arm was moved bythe operation of the glider I49. Since the yoke I59 of the slot arm I58is attached at I to the movable platform 96, any motion of the saidslotted arm will be transmitted through said yoke and means ofattachment to said movable platformand therefore any oscillatorymovement of the slotted arm I58 will be reflected by exactly similarmovement of the movable platform 96 and corresponding movement of theentire punching mechanism 56. The free mountings comprising slot I ofthe slotted arm I58 and the gliders I49 and I68 are provided, ratherthan fixed mountings, since the upper end of the slotted arm I58 at I60is not free to rotate in a circular arc but is required at all times byits attachment to platform 96 to move in a single plane. In order,therefore, to permit suchmovement of the end of the slotted arm in asingle plane while at the same time oscillating such arm about a fulcrumat I68 it is necessary to permit the arm to move relative to saidfulcrum. Likewise, the slot I65 and the glider I49 are required sincethe rotary motion of the arm I41 is to be converted into oscillatorymotion of the slotted arm I58 and a sliding of the glider I49 back andforthwith respect to the fulcrum of the arm I58 is thereby madenecessary.

It is now apparent that rotation of the shaft I43 produces by means ofthe arm I41 and the slotted arm I56, a corresponding oscillatorymovement of the movable platform 96 and of the punching mechanism 58.The speed of oscillation of the movable platform 96 and of the entirepunching mechanism 58 may be varied and adjusted byvariations in theplate I54 and the annular groove I53 and the distance betweenperforations or cut-outs made by punching. plate upon the moving web 53may be varied by varying the diameter of the circular plate I54 and thediameter of the annular groove I53 so that the distance covered by theplatform 96 during each oscillation of the slotted arm I58 and thecorresponding oscillation of the movable platform 96 will be increasedor decreased with respect to the moving web 53 and .thus space theperforations or cut-outs at a correspondingly different dis-.

tance from each other. The perforations or cutouts may thus be placed inseries closer to or at a greater distance from each other by acorresponding operation of reducing or increasing the diameter of thecircular plate I54. For this purpose, a series of circular plates I54having varying diameters must be provided.

The necessity for such a series of circular plates may be obviated byanother improved expedient associated with the rotatable arm I41hereinafter to be described.

The movement of the yoke portion I59 of the slotted arm I58 and thecorresponding movement of the movable platform 96 may be varied during asingle stroke so that the platform will move at the speed of the paperwhile the punching plate I09 is in contact with the web 53 and at otherspeeds as may be desired while the punching plate is not in contact withthe web 53. This may be accomplished by an eccentricity in the annulargroove I53, such eccentricity being placed for instance at I13 (Figs.and 12) and permitting variations in the speed of movement of the wheelI51 by reason of the fact that the effective radius of rotation of saidwheel I51 about the shaft I43 will be varied by the forcing of saidwheel by the annular groove either closer to the shaft I43 or furtheraway from it. Thus when the wheel I51 is traveling in the portion I13 ofthe annular groove I53, its speed will be decreased, the decrease ofspeed being a function of the relation ship of the radius at I13 to theradius a the annular groove at other portions thereof. Therefore, whilethe movable platform 96 is being thrust forward, the speed thereof willbe less than that of said platform during the return but will be equalto that of the web 53. Care must however be taken that the formation ofthe annular groove I53 is such that at all'times during the forwardthrust of the entire punching mechanism 58, the speed thereof is thesame as that of the web 53. The variation in speed of the return of thepunching mechanism by reason of the eccentricity of the annular grooveI53 thus provides for a resetting of the punching mechanism at theproper time and in the proper place for the next perforating operation.

In a preferred form of activating means for the slotted arm I58, it ispossible to omit entirely the circular plate I54 and the annular grooveI53. This form is shown in Figures 10, 11, 13 and 14 in which therotating shaft I43, Figures and 11, which corresponds exactly to therotating shaft I43 of Figure 8, has mounted at the other end thereof, arotating arm I14 which corresponds to the rotating arm I41 of Figure 5.The shaft I43 is rotated in exactly the same manner as the shaft I43 ofFigure 8 and the rotatable arm I14 securely aflixed thereto is likewiserotated thereby. v

A glider I15 similar in operation to the glider I49 is pivotally mountedat the end of the rotatable arm I14 and the rails thereof I16, I11capture the sides I81, I81 of the slotted arm I58 in exactly the samemanner. Likewise the piv-v otal mounting of the oscillating arm I58about its fulcrum isaccomplished by the glider I68 which corresponds tothe same member in Figures 5 and 8 and is pivotally mounted on thefixedshaft IGI.

The difference between the form thus illustrated in Figures 10 and 11and that illustrated in Figures 5, 8 and 12 is that the speed ofmovement of the slotted arm and the corresponding speed of movement ofthe entire punching mechanism 58 is not varied at any time during theperiod of operation, said speed being at all times a constant one.

It has been found by experiment that variations in the speed of movementof the punching mechanism, varying its oscillating period, are for mostpurposes both unnecessary and exceedingly difiicult to make; and that itis much simpler to cause the slotted arm and the corresponding platform96 to move continuously at all times at the same speed as the web 53.

Any variation in the distance between successive perforations orcut-outs may be accomplished by variations in the radius or length ofthe rotating arm I14 and corresponding changes in the period of theoscillation of the punching mechanism 58.

The preferred form shown in Figures 10 and 11 lends itself readily tovariations in the speed of oscillation of the punching mechanism 58without any difliculty or complicated adjustment.

Since, as has been above pointed out, the speed of oscillation of themovable platform 86 may be changed by changing the effective radius ofrotation of the arm I14 (Figure 10), that is, by bringing-the pivotedportion I18 of the glider I15 closerto the shaft I43 or further awaytherefrom, then any means associated with the rotating arm I14 whichwill cause said pivoted portion I18 and therefore the glider I15 to moveeither towards or away from the shaft I43 will be just as effective aschanging the length of the rotating arm I14 and will necessarily changethe speed of oscillation of the punching mechanism 58.

This may be readily accomplished by the apparatus shown in dotted linesin Figure 10 and in the cross-sectional view of Figure 32 wherein (seeFigures 13, 14 and 32) the pivoted portion I18 of the glider I15 issecured to a block I19 which is threaded at I88. T'he'block I19 is freeto slide within the channel I8I (Figures 13 and 32) of the rotatable armI14. A block I82 is fixedly secured by means of the bolts I83 (Figures14 and 32) within the channel I8I and to the body I14 of the rotatablearm. Said block I8! is perforated at I84. A bolt I85 having a head I86isinserted through the perforation I84, its movement relative to theperforation being impeded by the bearings I 81 and I88. The opposite endof the bolt I85 is threaded at I89, the threads ISIS being so formed asto match exactly with the threads I80. The head I86 of: the boltrotation by a tool of the head I86 will cause a corresponding rotationof the bolt I85 thereby turning the threaded portion I89 thereof whichwill in turn cause the block I19 to move in a direction corresponding tothe direction of rotation and which will thereby move the pivotedportion I18 along the rotatable arm I14 changing its distance from therotating shaft I43 thus changing the effective radius of rotationbetween the mounting of the rotatable arm I14 on its shaft and theglider-pivot I18 and the period and speed of oscillation of the movableplatform 96 and the punching mechanism 58.

It is of course necessary to synchronize the operation of the punchingplate I 69 of the punching mechanism 58 with the oscillatory movementof'the entire punching mechanism. To this end fasjhas been'heretoforedescribed, the punching plate I69 is 'mountednpon a slide III) which isstroke of the slide IIO of the punchingplate I09 be simultaneous withthe forward motion of the punching mechanism 58 and should be completedbefore the return of the punching mechanism 58 commences. It thusbecomes extremely useful to drive the punching plate itself from. thesame source of power that creates the oscillatory movement of the entirepunching mechanism 58 and it is desirable to simplify the operation ofmaking any necessary variations in the speed of oscillation of thepunching plate I09 when the speed of oscillation of the entire punchingmechanism 58 is changed.

Accordingly, the shaft I38 which drives the oscillating mechanism of theentire punching member58 also drives the shaft I by means of the bevelgears 202 and 203, the said shaft rotating in the bearings 204 and 205,the friction upon the shaft being minimized by the thrust bearing 205(see Figures 2 and 8). The bevel gear 201 at the opposite end of theshaft 20I drives the bevel gear 208 which in turn drives theconcentrically arranged gear wheel 209 which, through the idler 2I0,drives the gear wheel 2 which is mounted on the shaft 2I2, a spiralgear213 being mounted also on said shaft 2I2 (see Figures 2 and 8).

The rotation of shaft 20, therefore, through the gear train 201-2 IIthereby drives and causes the spiral gear 2 I3 to rotate. The spiralgear 2 I3 and its shaft 2I2 is mounted in the bearings 2H, 2 which inturn are supported on the posts 2I5, 2I5 which are fixedly supported bymeans of the bracket 2I6 on the frame of the machine so that the spiralmember, except for its rotation, has no movement whatsoever with respectto the entire machine and so that the punching mechanism 58 in itsoscillation within the machine also oscillates with respect to themounting of the spiral member 2I3.

spirals 2I3 and 2H.

It is essential to so. regulate the rotation of I the shaft H3 and thecorresponding oscillation of the punching plate I09 that any rotationthereof will correspond to the oscillatory movement of the entirepunching mechanism 58; that is, that the punching plate I09 will descendthrough the web 53 during the forward motion of the punching mechanism58 and so that the punching plate I09 will be free of the web 53 duringthe return of the punching mechanism.

It is thus found advantageous to cause the rotary motion of the shaft H3and the corresponding oscillatory. motion of the plate I09 to be afunction of the oscillatory movement of the entire punching mechanism.Thus as the punching mechanism 58 moves forward, the meshing of thesmall spiral gear 2" in the spiral 2I3 causes said spiral gear to rotateand thus causes a corresponding rotation of the shaft H3 and acorresponding oscillation of the punching plate I09.

If the path through which the entire punching mechanism 58 were to passand if the corresponding path of the spiral gear 2I'I upon the spiralgear 23 were sufficiently long, then no motion of the spiral gear 2 I3would be necessary to create a sufiicient rotation of the shaft H3 toeffect the punching operation. The motion of the small spiral gear 2"along the spiral gear 2I3 alone would result in a sufficient rotation torelease the spiral gear 2II from its .engagement with the spiral 2I3 inorder to prevent any undesired rotation ofthe shaft H3 in the undesiredopposite direction. l

However, it is found expedient to cause-the spiral gear 2I3 to rotate,said rotation .being preferably at least equal to or greater than thespeed which would be induced in the small spiral gear 2I'I by the returnmotion of the punching mechanism 58 so that at all times the rotation ofthe shaft II3 would be in the same direction. Where the speed ofrotation of the spiral gear 2I3 is equal to the speed that would beinduced by the return motion of the .smallspiral 2", then during thereturn of the punching mechanism 58, the small spiral 2I'I will merelyslide along the groove spiral gear 2I3 and the shaft H3 and the cam II5will remain poised in the up position so that the punching plate will befree of the web 53 during the return. The rotation of the spiral gear2I3 with respect to the small spiral gear 2II also produces anothereffect and that is that when the forward speed of the punching mechanism58 and the corresponding forward speed of the worm gear 2I'I is combinedwith the additional speed of rotation given to the spiral gear, then thestroke of the cam H5 and the corresponding stroke of the punching plateI09 at the time when it enters and rises from the web. is much fasterand much more forceful and rapid than would otherwise be the case werethere no rotation of the spiral gear 2I3; and correspondingly, since theeffective speed'of rotation of the spiral gear 2I'I during the return ofthe entire punching mechanism 58 is equal to the difference between thespeed of the spiral gear 2I3 and the speed of the return of the punchingmechanism 50, the stroke of the cam I I5 along the'upper portion of thearc is slower than the downstroke or cutting stroke. Thus, where, in thepreferred form, the speed of rotation induced in the small spiral 2I'Iby the return is equal to the speed induced by the rotation of spiral2I3. Then during the return of the punching mechanism, the small spiral2I'I will simply slide along the groove of the spiral 2I3, the shaft II3will not rotate and the cam II5 will consequently be virtuallystationary during the return so that the punching plate I09 will bepoised in the up position during the return.

The punching plate I09 and the die I26 may readily be changed to providefor different sizes and shapes of perforation or cut-out. It should benoted however, that where the same size perforation or cut-out isdesired, but where, however, a different space or distance between saidperforations is required in order to form bags or articles of differentsizes, the only manipulation that is necessary to effect a change in theoperation ofthe machine to increase the said dis- ,tance is themanipulation or rotation of the head I of the bolt I85 (Figure 32) comesin connection with change gear size connected with change of ratioinduced by difference in change gear 12. No other operation whatsoeveris required for this purpose, except that, as hereinafter described,changes in the size of the change gear I2 will produce different speedsof move-

